Safety circuit



G. STEIN SAFETY CIRCUIT May 31, 1966 Filed Nov. '7, 1963 INVENTOR 64/? Y STEIN ATTORNEY United States Patent Ofilice 3,253,583 Patented May 31, 1966 3,253,683 SAFETY CmCUIT Gary Stein, New Berlin, Wis., assiguor to Applied Power Industries, Inc, Milwaukee, Wis., a corporation of Wisconsin Filed Nov. 7, 1963, Ser. No. 322,18 7 Claims. (Cl. 192-3) This invention relates generally to a hydraulic system wherein several loads are placed in series with means to automatically effect a braking of an upstreamload upon a loss of pressure in the system or when a downstream load is receiving fluid power.

More specifically, one use of the invention relates to a hydraulic system for operating a hoisting winch in fluid series with other loads in a manner insuring that the hoisting winch is braked during a loss of pressure in the fluid system.

It is desirable from the viewpoint of circuit simplicity and manufacture economy to place several loads in series rather than to require a separate pump output for each load. Although many loads are powered serially, the workers in the prior art have found it necessary to provide a separate fluid supply for winches or similar apparatus because of the extreme danger caused by an uncontrolled load. In the embodiment described, the invention pertains to hydraulic circuitry which permits winches to be hydraulically placed in series with other functions such that a downstream function will not release the brake on upstream winches. It should be understood, however, that the invention is not limited to winch environments.

It is well known to provide safety mechanisms for hydraulically driven hoisting winches to insure that the winch does not rapidly urn-eel as a result of unwanted power loss. Such safety means are provided in many diflerent ways. The presently described invention provides a mechanism of positive safety which permits a hydraulically driven winch to be in series with downstream loads.

A further objective of this invention is to provide a spring actuated braking assembly for a winch which is under the control of a double acting hydraulic cylinder eflecting hydraulic braking or retarding are conveniently inserted along with the necessary pressure relief valves.

Another important objective of the invention is to provide a hydraulic system wherein the basic addition of an additional brake valve and an additional relief valve converts the system into one primarily for use with loadings which must be powered in two directions, and which could become dangerously out of control in either direction.

These and other important objectives and advantages of the invention will be more fully understood upon a reading of the following specifications, taken in view of the attached drawings, in which:

FIGURE 1 is a diagrammatic-schematic of one embodiment of the system; and

FIGURE 2 is the embodiment of FIG. 1 including a further refinement.

Referring now to the drawings, the numeral 10 indicates the system of this invention. The system includes a pump 12 having an output conduit 14 leading therefrom and an input conduit 16 in communication with a reservoir R. A conduit 13 leads from conduit 14 to reservoir R across a high pressure safety relief valve 15.

The conduit 14 is also communicated with a conduit 18 which leads to a piston rod chamber 20 of a double acting hydraulic cylinder 22. The cylinder includes a piston head expansion chamber 24 which is communicated by conduit 26 to a conduit 27, the high pressure carryover or downstream line. The conduits 18 and 26 represent lead and return lines for actuation of a piston 28.

Extending from piston 28 is a piston rod 30 terminated by a brake shoe 34 at its outer end. A spring 32 around rod 30 normally biases the brake shoe 34 toward a mating brake shoe 36. A cable is coiled about the winch assembly 42 to which loads of varying types are attached. The brake mechanism operates on the hydraulic motor output shaft ahead of the gear box since this is the area of lowest torque. The winch assembly includes a mechanical gearing box 44 driven by an output shaft 46 of a hydraulic motor 48.

It can be seen that output conduit 14 leads to a manually operated direction valve 50 comprised of a first segment A, a second segment B, and a neutral segment N. In FIGURE 1 the valve is depicted as being in its neutral position. Leading from valve 50 is a conduit 52 which delivers fluid for driving motor 48 in a first direction and a conduit 54 which delivers fluid for driving the motor in the opposite direction. It should be understood, of course, that directional changes in motor 48 cause either the reeling or unreeling of cable 40. In FIGURE 1, a load attached to the cable 40 is lifted when the direction of fluid is toward motor 48 in line 54; that is, when segment A is across lines 52 and 54.

Assuming for purposes of illustration that segment A of valve 50 is across conduit 14, forward fluid flow to motor M is through conduit 54 and principal return how to valve 50 is through conduit 52. A one-way check valve 68 prevents any return flow via conduit 54. When segment B of valve 50 is across the conduit system, the winch will unreel as a result of a fluid flow toward motor 48 in conduit 52. A braking valve 56 across conduit 57 provides a return path for fluid to passageway 59 of valve 50. When lowering a heavy load, the motor 48 will have a tendency to act as a pump. In order to avoid cavitation and loss of control, a pressure sensing line 58,.-from conduit 52 to the expansion head of control cylinder 61, will control-the speed at which the cable is permitted to unreel.

In order to eliminate pressures in excess of circuit design, a relief valve 62 is provided. This valve transmits excess pressures from the fluid line 54 leading from the motor directly back to conduit 52. Valve 62 relieves excess pressures primarily when valve 50 is in neutral or the load is being lowered too fast.

Regardless of the direction of operation of Winch 40, the returning fluid reaches a point 65 Where conduits 26 and 27 are joined. Fluid under pressure at this point is directed toward a direction valve 72 and thence to a further downstream function. Other downstream functions can be sequentially connected in series via the conduit 74.

With equal pressures in lines 18 and 26, the spring 32 is of suflicient strength to brake the winch. Upon a movement of either of the segments A or B of valve 50 across the line 14, pressure build-up in conduit 18 causes piston 28 to move away from the winch assembly. Since there is a fluid pressure drop caused by powering the winch, there is a corresponding drop in pressure at point 65 which is reflected in chamber 24. Thus, the brake is released during periods in which the winch is reeling or unreeling. When the valve 50 is in neutral,

the pressure drop across valve 50 is insuflicient to cause spring 32 to reduce its braking function.

When valve 50 is in neutral and pressure is generated by a load controlled by valve 72, such pressure build-up will be reflected in conduits 27, 14, 18 and 26. Upon such a build-up or of a loss of pressure in conduit 27, the brake cylinder 22 will not'release the brake because the same pressure loss will occur in 14, 18 and 26. The cylinder 22 is so constructed that the spring 32, the pressure drop across segment N of valve 50, and the pressure area diflerentials of facing chambers 20 and 24, will prevent the release of the brake upon a movement of valve 50 from neutral.

In other words, the spring 32 and the pressure in chamber 24 (determined by the pressure drop between line 14 and point 65) is suflicient to maintain the brake in its restraining position when the valve 50 is in neutral. When either of the segments A or B is moved across the lines 50 and 54 the pressure drop increases suificiently to permit the pressure in chamber 24 to overcome the spring 32, Therefore, regardless of variations in downstream pressures, the pressure drop between line 14 and point 65 is determinative of braking or non-braking.

FIGURE 2 discloses how the inventive system described herein is adopted for use in environments where it is important to control and brake loads in two directions. For instance, shaft 46 could be the power output to a pedestal of a rotating crane. There are many instances, such as a sloping platform, where the weight of the crane could cause the motor '48 to act as a pump. Because of this it will be noted that a one-way check valve 68 has been placed across conduit 52, an additional braking valve 56' between line 52 and valve 50, a control cylinder 61 for controlling valve 56', and an additional sensing line 58'. The addition of the above elements permits the system to protect itself from excess pressures and uncontrolled loads when segment B is across the power in the same manner as previously described for segment A.

Insofar as the braking action on shaft 46 is concerned, it is identical because the pressure drops through valve 50 and elsewhere remain the same.

In a general manner, while there has been disclosed eflec'tive and eflicient embodiments of the invention, it should be well understood that the invention is not limited to such embodiments, as there might be changes made in the arrangement, disposition, and form of the parts without departing from the principle of the present invention as comprehended within the scope of the accompanying claims.

I claim:

1. A system for operating and braking a work member, a brake having a first position restraining the movement of said member and a second non-restraining posi-' necting said piston to said brake, a source of fluid pressure, a hydraulic motor for operating said work member, a fluid conduit system communicating said source to said motor, including a first line directing the fluid from said source to said motor and a second line directing said fluid from said motor, a third line communicating the pressures in said first line with said first expansion chamber, and afourth line communicating the pressures in said second line to said second expansion chamber, a directional valve having a first position permitting fluid to flow to said motor and a neutral position routing said fluid directly to said second line, said first means being of sufficient strength to maintain said brake in said restraining position when said valve is in said neutral position, and insuificient to maintain said brake in its said restraining position when said valve is in said first position.

2. A system for fluid powering and braking a work -member and powering a downstream load in series with said work member, a conduit leading to said downstream load, a valve having at least one position for transmitting fluid to said downstream load, a braking member movable from a work member restraining position to a work member non-restraining position, first means normally biasing said member to said restraining position, a source of fluid pressure, a fluid motor drivingly connected to said work member, a conduit network between said source and said motor, a second valve across said network having a first position transmitting fluid to said motor and then to said downstream load and a second position transmitting fluid directly to said downstream load, said first means being of sufiicient strength to maintain said brake in said restraining position when said valve is in said neutral position, and insuflicient to maintain said brake in its said restraining position when said valve is in said first position.

3. In a system for operating and braking a work member, a brake for impeding movement of said work member, a spring for normally actuating said brake, a fluid pressure cylinder having a piston connected to brake, a fluid pressure source, a fluid motor for driving said member, a downstream load, a conduit leading to said downstream load, a valve having at least one position for transmitting fluid to said downstream load, a valve having a first position sending said fluid to said motor and then to said load and a second position routing fluid directly to said downstream load, a first pressure drop developed when said valve is in said first position, a second pressure drop developed when said valve is in said second position, said first means being of sufficient strength to maintain said brake in said restraining position when said valve is in said neutral position, and insuflicient to maintain said brake in its said restraining position when said valve is in said first position. l

4. A system for fluid powering and braking a cable drum and powering'a downstream load in series therewith, a braking member movable from a drum restraining position to a drum non-restraining position, first means normally biasing said member to said restraining position, a source of fluid pressure, a fluid motor, a conduit network between said fluid source, said motor and said downstream load, a valve across said network having a first position transmitting fluid to said motor and then to said downstream load and a second position transmitting fluid directly to said downstream load, a double acting cylinder responsive to the diflerential in pressure drops when said valve is in said first and second positions for moving said brake to its restraining position when said valve is in said second position.

5. The system described in claim 4 wherein said cylinder has first and second expansion chambers, a first conduit communicating the fluid pressure at the entrance to said valve to one of said chambers, a second conduit communicating the fluid pressure as it departs from said valve, the pressure at said entrance working in opposition to said first means.

6. A system for fluid powering and braking a work member and powering a downstream load in series with said work member, a braking member movable from a work member restraining position to a work member nonrestraining position, first means normally biasing said member to said restraining position, a source of fluid pressure, a fluid motor, a conduit system between said fluid source, said motor and said downtream load, a valve across said system having a first position transmitting fluid to said motor and then to said downstream load and a second position transmitting fluid directly to said downstream load, second means responsive to the difierential in pressure drops when said valve is in said first and second positions for moving said brake to its restraining position when said valve is in its second position, a braking valve in said conduit system between said motor and said first mentioned valve.

7. The system described in claim 6 wherein third means References Cited by the Examiner UNITED STATES PATENTS 7/1960 Rye 19 2 3 4/1962 Kocalis 254-184 DAVID J. WILLIAMOWSKY, Primary Examiner. 

1. A SYSTEM FOR OPERATING AND BRAKING A WORK MEMBER, A BRAKE HAVING A FIRST POSITION RESTRAINING THE MOVEMENT OF SAID MEMBER AND A SECOND NON-RESTRAINING POSITION, FIRST MEANS TO NORMALLY URGE SAID BRAKE TO ITS RESTRAINING POSITION, A HYDRAULIC CYLINDER, A PISTON SLIDABLY RECEIVED IN SAID CYLINDER AND DEFINING FIRST AND SECOND EXPANSION CHAMBERS WITH SAID CYLINDER, SECOND MEANS CONNECTING SAID PISTON TO SAID BRAKE, A SOURCE OF FLUID PRESSURE, A HYDRUALIC MOTOR FOR OPERATING SAID WORK MEMBER, A FLUID CONTROL SYSTEM COMMUNICATING SAID SOURCE TO SAID MOTOR, INCLUDING A FIRST LINE DIRECTING THE FLUID FROM SAID SOURCE TO SAID MOTOR AND A SECOND LINE DIRECTING SAID FLUID FROM SAID MOTOR, A THIRD LINE COMMUNICATING THE PRESSURES IN SAID FIRST LINE WITH SAID FIRST EXPANSION CHAMBER, AND A FOURTH LINE COMMUNICATING THE PRESSURES IN SAID SECOND LINE TO SAID SECOND EXPANSION CHAMBER, A DIRECTIONAL VALVE HAVING A FIRST POSITION PERMITTING FLUID TO FLOW TO SAID MOTOR AND A NEUTRAL POSITION ROUTING SAID FLUID DIRECTLY TO SAID SECOND LINE, SAID FIRST MEANS BEING OF SUFFICIENT STRENGTH TO MAINTAIN SAID BRAKE IN SAID RESTRAINING POSITION WHEN SAID VALVE IS IN SAID NEUTRAL POSITION, AND INSUFFICIENT TO MAINTAIN SAID BRAKE IN ITS SAID RESTRAINING POSITION WHEN SAID VALVE IS IN SAID FIRST POSITION. 